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3-4 Pinch Point Calculation 29 evaluate this incidence loss for radial gas turbines. However, due to lack of literature available on the evaluation of incidence loss for organic fluids, the nominal design point efficiency has been considered to be the isentropic efficiency. ^^hDWd/KE^ ^/'E s>h^ /EWhd^ &ZKD z> dDWK ^hZKhd/E Z/> dhZ/E >h>d ZWD ^W/&/ WKtZ ^W/&/ /DdZ ^W/&/ ^W &&//Ez KhdWhd dK z> dDWK ^hZKhd/E ^hZKhd/E EK>/E ZKdKZ/E ^hZKhd/E ZKdKZKhd ^hZKhd/E dhKhd>d W d ^ Figure 3-12: Architecture of the Radial Turbine Model implemented in Fortran Figure 3-12 illustrates the architecture of the radial turbine model discussed above. The model can be chosen by a unique identification code in Cycle-Tempo. The input values of the cycle are provided from Cycle-Tempo into the main subroutine. The assumptions and design values are also input to this subroutine. Each station of the turbine has been implemented in a different subroutine and these interact by passing the required parameters to each other. The details of the calculation procedure and the individual subroutines can be found in appendix B. 3-4 Pinch Point Calculation The most critical components apart from the turbine are the heat exchangers. Although a detailed heat exchanger design is out of the scope of this work, it is however essential to make sure that the heat exchangers operate in accordance with the second law of thermodynamics. Hence a pinch point analysis of the heat exchangers present in the system has been done The pinch point is defined as the point at which the temperature difference between the hot and the cold fluid is minimum. The system has four heat exchanging equipments which need to comply to the second law of thermodynamics. The pinch points in the regenerator and the condenser are defined by their terminal temperature differences which are given as inputs to the system model. However, in case of the evaporator, the pinch point can be either at the lower temperature terminal or at the saturated temperature (in sub-critical cycles) or at point where the slope of the curves are equal (in supercritical cases). Figure 3-13(a) and Figure 3-13(b) illustrate typical T-Q diagrams for the evaporator in subcritical and supercritical cycles respectively. Master of Science Thesis Akshay HattiangadiPDF Image | Working Fluid Design for Organic Rankine Cycle
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